Variable speed transmission



Speed RAT/0 4 Sheets-Sheet l W. L. POLLARD VARIABLE SPEED TRANSMISSION w fi M? .4

April 1944- w. L. PouLAn Re. 22,466

VARIABLE SPEED TRANSMISSION Original Filed Dec. 13, 1940 4 Sheets-Sheet 2 April 4, 1944.

W. L. POLLARD VARIABLE SPEED TRANSMISSION Original Filed Dec. 13, 1940 4 Sheets-Shet 5 -April 4, 1944. w. POLLARD VARIABLE SPEED TRANSMISSION Origin a1 Filed Dec. 13, 1940 4 Sheets-Sheet 4 7 m A a/ff A, "I MMWW///// AAMM aw 4 m, y 6 F Z i H Reiuued Apr. 4, 1944 Original No. 2,301,451, dated November 10, 1942,

Serial No. 370,045, December 13, 1940. Application for reissue November 6,1943, Serial No.

.16 Claims. Cl. 74189-5) "My invention relates to variable speed transmissions.

One of the objects of my invention is to provide an improved. hydraulic torque converter transmission with improved means whereby under one condition power may be transmitted from a drive shaft to a driven shaft along two parallel paths, one of which includes the hydraulic torque converter, and whereby under another condition all of the power may be transmitted through the hydraulic torque converter.

shift in a plural stage hydro planetary transmission.

Further objects and advantages of the'invention will be apparent from the description and claims.

In the drawings, in which several forms of my invention are shown,

. Figure 1 is an axial section showing a combination hydraulic torque converter and planeta y ear drive;

Fig. 2 is an axial section showing another form;

Fig. 3 is an axial form;

Fig. 4 is an axial section showing a control apparatus which may be substituted for part of the control apparatus of Fig. 3; g Fig. 5 is an axial sectional view showing ansection showing another other control apparatus which may be subst tuted for part of the control apparatus shown in ms. 3;

Fig. 6 is a chart of efliciency, torque, and speed curves:

Figs. '7, 8 and 9 are axial sectional views of other forms of my invention; 1

Fig. 10 is a chart showing efliciency and torque curves plotted against relative speeds; and

. Figs. 11, 12-, 13, 14, 15 and 16 are axial sectional views of other forms of my invention.

which an overdrive may Referring to the drawings in detail, and first to Fig. 1, the construction shown comprises a drive shaft l, a driven shaft 2, an intermediate shaft 3, a hydraulic torque converter comprising a pump rotor 4, a one-way rotatable stator 5, a turbine rotor 6 keyed to the intermediate shaft, a front planetary comprising. a planet carrier 1 keyed to the drive shaft l, a sun gear 8 keyed to the intermediate shaft 3, a ring gear 9, planet gearing Ill carried by the gear carrier I and mesh ing with the sun gear 8 and ring gear 9, a dual clutch comprising a casing II rotatable with the pump rotor l, a clutch disc [2 splined on the gear carrier 1, a clutch disc I: splined on the'ring gear 9, clutch means l4 whereby either one of the clutch discs may be. connected to rotate with the casing l i and pump rotor I, and a rear planetary construction comprising a gear carrier l5 keyed to the intermediate shaft 3, a sun gear I6 rotatable with the one-way stator 5, a ring gear I! keyed to the driven shaft 2, planet gearing i8 carried by the gear carrier l5 and meshing with the sun gear I6 and ring gear H, a one-way anchorage device IQ for preventing reverse rotation of the one-way stator 5, and a one-way clutch 20 for preventing the one-way stator from overrunning the turbine rotor.

In this construction, if the dual clutch is set to connect the pump rotor l with the'gear carrier 1, the entire power flow will pass through the hydraulic torque converter to the intermediate shaft 3, giving a relatively high torque ratio. The torque from the intermediate shaft 3 will be transmitted through the gear carrier ii to the planetary gearing [8. This will cause force to be exerted in the direction of rotation of the intermediate shaft 3, both on the sun gear l6 and on the ring gear II. This will cause rotation of the driven shaft. When the torque ratio becomes such that the torque exerted on the sun gear It by the planet gear becomes greater than the reverse torque exerted on the one-way stator 5 bythe fluid action, the one-way stator will begin to rotate and the hydraulic part of the transmission will cease to act as a converter and will then act as a coupler.- This eliminates a drop 'in the efliciency curve, as explained in my co-pending application Serial No. 308,668, filed December 11, 1939.

If the dual clutch is operated to disconnect the pump rotor 4 from the gear carrier I and connect it with the ring gear 9, the power flow from the drive shaft l to the intermediate shaftli will be divided into two paths. One path will be stator andturbine rotor 3 to the intermediate shaft 3. gearing Ill through the sun gear 3 to the intermediate shaft. This "will result in an increase in the overall efiiciency'between the drive shaft and the intermediate shaft as a large proportion of the power is by-passed around the torque converter.

The construction shown in Fig. 2 is similar to that shown in Fig. 1 except that a dual twin disc clutch is provided for eliminating the premature transformation action and giving a higher final torque ratio, that a brake is provided for giving an overdrive, and a shift is provided for enabling a reverse to be obtained. In the twin disc clutch construction, the clutch casing 2i is rotatable with the sun gear i6 and canbe alternatively connected, either with the one-way stator 5 or with the intermediate shaft 3, by means ofthe clutch discs 22 and. When the clutch casing 2i is connected with the clutch disc 23, the sun gear ii is secured to rotate with the intermediate shaft 3 and as the gear carrier l5 also is secured to rotate with the intermediate shaft, the.

planetary construction will rotate as a unit, so that the shaft 2 will be driven at the same speed as the shaft 3.

For overdrive, the clutch discs 22 and 23 are both freed and a brake 2! is applied to the clutch casing 21 to hold the sun gear l3 against rotation to effect an overdrive of the ring gear l1 slidably keyed to the final driven shaft 2.

For reverse, the entire planetary construction.

can be shifted bodily .rearwardly to connect the gear carrier IS with the. stationary dog clutch ring 28 and to free the gear carrier from the intermediate shaft 3. The twin disc clutch will be positioned to connect the clutch casing 2| with the clutch disc 23 so that the sun gear IE will rotate with the shaft 3. Under these conditions,

the gear carrier I5 is held against rotation, the

sun gear 15 rotates with the shaft 3, and the ring gear I! and final driven shaft 2 rotate in a reverse direction and at a lower-speed than the intermediate shaft 3.

In the construction shown in Fig. 3, the drive shaft I, the pump rotor l, the stator 5, the turbine rotor 6, the gear carrier 1, the sun gear 8, the ring gear 9, the clutch casing II, the clutch discs i2 and I3, and the one-way anchor l9 may be similar to those previously described. In Fig. 3, however, the clutch disc I3 is splined on the sun gear 8 instead of on the ring gear 9, as shown in Figs. 1 and 2. and in Fig. 3 the shaft 3 iskeyed to the ring gear 3 instead of to the sun gear 3.

' .as shown in Figs. 1 and 2. In addition, a brake drum 2'! is secured to the sun gear 8 so. that when desired the sun gear 8 may be held against rotation by application of the brake shoe 28 to the brake'drum. 21. with this construction three different driving conditions may be obtained. If the member II is applied to connect gear a to the shaft 3, the other path being from The other path will be from the planet p 22,466 *irom the ring gear 3 through the pump rotor gear 8, clutch plate [3, clutch housing ll, pump rotor 5, stator 5, and turbine rotor 3 to the shaft 3. Under this condition, the ring gear 3 acts as an efficiency booster in icy-passing a largeproportion of the power around the hydraulic transmission.

For overdrive, both clutch plates 12 and I3 are disconnected and the brake shoe 2B is applied to hold the sun gear 3 against rotation. Under these conditions the hydraulic action is entirely eliminated, the entire power flow being from the gear carrier 1, through planet gearing ill and 8 against rotation. The clutch means shown for this purpose comprise a clutch casing 30 keyed to the sun gear 3, a clutch disc 3|, splined to the casing of the pump rotor l, and an anchor disc 32 splined to a nonrotatable anchorage member 33.

In this construction also there are three different power flow conditions similar to those of the constructionof Fig. 3. When both of the discs- 3i and 32 are free, the entire power flow is from the gear carrier I, through the one-way clutch,

pump rotor easing, pump rotor 4, stator 5, andturbine rotor 5 to the turbine shaft 3. Under the condition in which the clutch plate 3i is connected to cause the pump rotor 4 to rotate with the sun gear 8, the power flow is divided, one path being from the gear carrier 1, through the ring gear 9'to the driven shaft 3, and the other path being from the gear carrier I through the planet gearing i0, sun gear 8, clutch casing 30, clutch disc 3|, pump rotor Lstator 5, and turbine rotor 6 to the driven shaft 3.

For overdrive, the clutch disc 31 is released,

and the friction disc 32 is placed in condition to ,hold the sun gear 3 against rotation. Under this condition, the hydraulic action will be eliminated and an overdrive will be eifected from the gear carrier I through the planetary Ill and ringgear '9 to the driven shaft 3.

In Fig. 5 is shown a. construction which may be substituted for the brake drum 21 and brake shoe 28 shown in Fig. 3. This construction comprises a clutch housing 34 keyed to the sun gear 8, a

clutch disc 35 splined to the drive shaft I, an anchorage plate 33 splined to' a nonrotatable anchorage member 31, and a disc controller 38 by means of which the clutch casing 3| may be connected, either to the clutch disc 35 or to the anchorage disc 35. With this construction, an ad- 1 dition to the three conditions outlined with respect to the construction of Fig. 3, another condition is possible, in that the sun gear 8 can be secured to rotate with the drive shaft I, thus effecting a direct drive with the hydraulic action eliminated.

. planetary combinations shown are indicated in the gear carrier I to the planet gearing ll, sun

dotted lines.

The construction shown in Fig. '1 comprises a drive shaft I, a driven shaft 2, an intermediate shaft I. a pump rotor I keyed to the drive shaft I, a one-way rotatable stator I. a turbine rotor 5 driven from the pump rotor 4, a sun gear 35 keyed to the intermediate shaft 3, a ,gear carrier 40 keyed to the driven shaft, planet gearing ll mounted on the gear carrier 45 and meshing with the sun gear 35, a ring gear I! meshing with the planet gearing, clutch means II for connecting and disconnecting the ring gear 42 with respect to the turbine rotor l,c1uix:h means N for connecting and disconnecting the intermediate shaft 3 with respect to the drive shaft I, one-way an- .chorage means 45 for holding the stator 5 against reverse rotation, a oneway clutch 48 for preventing the stator 5 from overrunning the turbine rotor 5, a one-way clutch 41 for preventing the turbine rotor 6 from overrunning the intermediate shaft 5, a one-way anchorage device 48 to prevent the reverse rotation of the ring gear, a one-way clutch 45 to prevent the ring gear 42 from overrunning the turbine rotor 5, a one-way clutch III to prevent the intermediate shaft 3 from overrunning the drive shaft'i, and a centrifugal clutch which enables the turbine rotor 5 to be connected directly with the pump rotor I when a certain speed of the turbine rotor is obtained. This construction may be suitable for a truck drive where very high torque is occasionally required. The two clutches l3 and 44.

may be operated to provide three different driving conditions. For extremely high torque, the clutch I3 is disconnected to allow the ring gear I! to rest against the one-way anchor 45 and the clutch 44 is placed in position to free the intermediate shaft 3 from the drive shaft I. these condtiions, the ring gear 42 is held against reverse rotation and the entire power flow is from ,the drive shaft I through the pump rotor 4, stator I. turbine rotor 5, one-way clutch ll, intermediate shaft I, sun gear 35, planet gearing II, and gear carrier 40 to the driven shaft 2. If the torque converter gives a torque multiplication of 4:1 and the planet gearing gives a torque multi- I! will be through the one-way clutch 41 and shaft 3. Since both the sun gear and-ring gear are caused to rotate with the turbine rotor, the ultimateeflect is that the gear carrier II also rotates with the turbine rotor. If the hydraulic transmission has a torque ratio of 4:1,this will give a torque ratio of 4:1 between thedrive shaft I and. the driven shaft 2. Under this condition.

the sun gear I acts as an efficiency booster, as it by-passes, a, substantial portion of the power .aroundthe hydraulic transmission.

Under the third condition the clutch 43 is placed in position to connect the ring gear 42 to rotate with the turbine 5 and the clutch 44 is placed iiiposition to connect the intermediate shaft I to rotate with the drive shaft I.

will give a lower torque ratio than that outlined V with the second condition, but will result in an increase in emciency as only a portion of. the power flow is throguh the moderately eflicient This Under I hydraulic transmission, the other portion ofthe povtvher flow being through a more highly emcient pa The flow from the drive shaft I to the driven shaft 2 through the hydraulic transmission is from the pump rotor 4 through the stator 5, tur- =bine rotor I, clutch 45, ring gear 42, planet gearing ll, and gear carrier 60. The other path is from the drive shaft Ithrough the clutch plate 44, intermediate shaft 3, sun gear 39, planet gearing II, and gear carrier III to the driven shaft.

The construction shown in Fig.8 is similar to that shown in Fig. 7, except that the relations of the sun gear and ring gear are reversed, and that a premature transformation efliciency booster is provided in combination with the hydraulic transmission. In Fig. 8 the clutch disc 43 is splined to the sun gear 39 instead of to the ring gear 42, as in Fig. 7, and the intermediate shaft 3 is keyed to the ring gear I! rather than to the sun gear as shown in Fig. 7.

The premature transformation efllciency booster construction shown comprises a gear carrier 52 rotatable with the drive shaft I, planet gearing 53 mounted on the gear carrier 52, a ring gear 54 meshing with the planet gearing 53 and rotatable with the pump rotor l, a sun gear 55 meshing with the planet gearing 53, a clutch casing 58, a clutch plate 51 for connecting and disconnecting the intermediate shaft 3 with respect to the drive shaft I, and a brake drum 58 and brake shoe 59- for holding the sun gear 55 against transmission from torque'conversion action to' coupling action results because of the fact that as soon as the torque, due to the pressure of the planet gearing 53 an the sun gear 55 mcomes greater than the reverse torque acting on the one-way stator I, the one-way stator 5 will begin to rotate and thereafter the hydraulic transmis sion will act as a coupler rather than as a converter. v

The clutch construction 55 and 51 of Fig. ac

complishes a result similar to that accomplished by the clutch ll of Fig. 7 in that it connects the intermediate shaft 3 to rotate directly with the drive shaft I, thus by-passing a large proportion of the power through the ring gear 52, planet gearing II, and gear; carrier MI to the driven shaft 2. For overdrive the clutch plate 51 is released and the brake shoe 5! is applied to hold the sungear 55against rotation to eflect overdrive of the ring gear 54. This overdrivemay be used either with the clutch 3 connecting the sun gear 39 to rotate with the turbo-rotor 5, or with the clutch 43 released to enable the sun gear to rest back on the one-way anchor 48.

In general, the e fiect is that the maximum torque obtainable from the construction of Fig. 8 is less than the maximumtorquc obtainable with that'of Fig. 7 on the one hand, but that theeiliciency when the divided. power flow. paths are used is higher than in that of Fig. 7, since a smaller proportion of the power is caused to flow through the moderately eilicient hydraulic transdriven in .a reverse the driven shaft 2.

construction of Fig. 7. k 1

The construction shown in Fig. 9 is similar to that shown in 'Figs. 7 and 8, except that here the clutch connection between the turbine I and one of the gears of the planetary transmission is I eases mission in the construction of Fig. 8 than in the greatly from 90 per cent and a torque curve which will drop from approximately 4 to 1.

In Fig. 11 is shown a construction similar in some respects to the construction shown in Fig.

omitted, the sun gear 39 being connected to ro- I tate with the turbine rotor Ii by means of the tubular shaft 62. In theconst'ruction of Fig. 9 only twodriving conditions are obtainable. In one condition, for maximum torque, the clutch I4 is operated to free the intermediate shaft 3 from the drive shaft I; Under this condition,

. both the sun gear 39 and the rin gear I! are connected indriven relation with respect to the turbine rotor 6, the ring'gear 42 being driven from the turbine rotor 8 through the one-way. clutch 41 and intermediate shaft 3, and the sun gear 39 as previously described being always ro' tatable with the turbine rotor 6.

For a lower torque, higher efilciency condition, the clutch 44 is operated to connect the intermediate shaft 3 with the drive shaft I. these conditions, the intermediate shaft 3 will travel ahead of the turbine rotor 6 so that the sun gear 39 only will be driven from the turbine rotor. This will give an efllcient drive, as the major portion of the power-flow is by-passed around the hydraulic transmission.

' In Fig. 8 the-gear carrier 43 and ring gear 42 may be slidably splined on the shafts I and 3, respectively, and a stationary gripping ring 490 may be provided for cooperation with a'c'orrespending gripping ringon the gear carrier ll.

With this construction, for reverse, the gear carrier l and ring gear 42 may be shifted rearwardly' to disconnect the gear carrier ill from the driven shaft 2 and connect it with the fixed gripping ring 43a and to disconnect the ring gear from its splined connection with the shaft] and connect it with the driven, shaft 2. Under these conditions, the gear carrier is held against rotation, the sun gear is connected to rotate with the turbine rotor and the ring gear 43 will be direction, carrying with it In the construction of m. 9, if desired, the

Under 1, in which the by-pass power flow is through the sun gear but providing for an overdrive. In

this construction, the parts I, I, l, 3,- I, I9, and IIImaybesimilartothoseshowninFig. 1. The

planetary part of the transmission comprises a gear carrier 93 keyed to the drive shaft l, two

sets of planet gears 34 and '5 mounted on this gear carrier 33, a sun gear 60 meshing with the planet gears 65, a one-way clutch 61 for preventing the sun gear 68 from overrunning the turbine shaft 3, a sun gear 89 meshing with the planet gears 64, a brake drum '9 and brake shoe II for holding the sun gear 89 against rotation for overdrive of the ring gear I2 which meshes with both sets of planet gears II and 65, a centrifugal clutch II by means of which connection may be effected between the ring gear I! and the pump rotor l, and a one-way clutch I4 for preventing the gear carrier from overrunnlng the pump rotor.

' With this construction, there are three possible driving conditions: (1) the brake drum '9 may be free to rotate and the centrifugal clutch I3 may be disconnected; (2) the brake drum 89 may be free and the centrifugal clutch I3 connected: and (3) the brake drum 69 may be held against rotation and Under the first condition, the drive will be I from the gear carrier 63 through the one-way clutch I4, pump'rotor l, stator 5, and turbine rotor 9 to the shaft 3. Under the second condition, there will be a divided power flow between,

. shafts I and 3, one path being from the gear rear end planetary of Fig. 8 may be substituted so that the construction of Fig. 9 also will be provided with a reverse drive for the driven shaft 2. I

Im the construction of Figs. 8 and 9, if desired. the rear end planetary gear of Fig. 7 may be substituted for the rear and planetary gear shown so-that the ring gear 42 will be connectible and disconnectible with respect to the turbine rotor 3, and the sun gear 39 will be keyed to the intermediate shaft 3.

The chart in Fig. 10 shows approximately the torque and efliciency curves which may be obtained from the constructionshow'n in Fig. 7', basedon the normal efiicien'cy and torque curves of the torque converter working alone, In the curves shown, it is assumed that the clutch will be disconnected during approximately. the lower third of the speed ratio range, giving a torque curve which drops from approiimately 12 to approximately 4 and an emciency curve start: ing Macro and rising to above iiii per cent. For the upper two-thirds ofthe speed ratio range. it is assumed that the clutch disc 44 is in position to connect the intermediate shaft 3 to rotate with the drive shaft I for lay-pass power flow,

carrier 63 through the planet gears 65, sun gear 66, and one-way clutch 81 to the shaft 3, and the other path being from the gear carrier 63 through the planet gears 65, ring gear I3, centriiugal clutch 'I3, pump rotor 4, stator i, andturbine 8 to the shaft 3. Under the third condition, the flow will be from the gear carrier 63 through the planet gears 65, ring gear I2, centrifugal clutch I3, pump rotor l, stator II, and

turbine rotor 6 to the shaft 3, the one-way stator v I revolving with the pump rotor 4 and turbine rotor 3, and the ring gear I2 being .overdriven with respect to the gear carrier 63 by reason of the fact that the sun gear." is held against rotation.

In Fig. 12, the hydro planetary construction is similar ,to that shown in Fig. 11, the parts I, 3, 4, I, 6, II, III, 83, B4, II, 98, B1, 88, 12, I3, and I4 corresponding to similarly numbered parts of Fig. 11. In Fig. 12, however, provision is made for prematuretransformation of the hydraulic transmission from torque conversion action to coupling action.

In Fig. 12, provision is made for connecting and disconnectingthe sun gear with respectto the V in another condition, the housing 11 may be congivin'gan efiiciency curve which will not vary nected with the clutch plate 19 splined to the hub of the one-way stator. This construction is operable under four different conditions:- (1) the clutch casing 11 may be left free to rotate and the centrifugal clutch 13 may be disconnected;

and (4) the clutch may be operated to hold the sun gear 53 against rotation with the centrifugal clutch 13 still connected.

Under the first condition, the power flow will be from the gear carrier 83 through the one-way 'clutch 74, pump rotor 4, stator 5, and turbine 6 to the shaft 3. Under the second condition, there will be a divided power flow, one path being from the gear carrier 53 through the planet gears 5,

' a sun gear 55, and one-way clutch G7 to the shaft 3, and the other path being from the gear carrier 53 through the planet gears 65, ring gear 12, centrifugal clutch l3, pump rotor 4, stator 5, and turbine rotor to the shaft 3. Under the third condition, the sun gear 63 will be connected to the one-way stator 5 to effect a premature transformation. Under these conditions, as soon as the forward torque on the sun gear 53 overcomes the reverse torque on theoneway stator 5, the one-way stator 5 will start to rotate, eliminating the torque conversion ac-- tion and transforming it to coupler action. Under the fourth condition, the power flow will be from the gear carrier 53, through the planet gears 65, ring gear .12, centrifugal clutch l3,

'pump rotor 4, stator 5, and turbine rotor 15 to way clutch 41, shaft 3, sun gear 33, planet gears 4|, and gear carrier 40 to the driven shaft 2.

with the construction shown in Fig. 13, assuming that the torque converter per se will give a torque increase of 3:1 and that in both planetaries the ratio of sun gear diameter to ring gear diameter is 2:3, with the transmission in lowthat is, with. both clutches 43 and 33 disconnected-a torque range of from about 5.5:1 to about 2.521 may be obtained, approximately 60 per cent of the power flow being through the fluid transmission, the other 40 per cent being by- P ssed.

For the intermediate speed range, the clutch 43 is connected, the clutch 83 remaining disconnected. Under these conditions, the ring gear 42 rotates in unison with the turbine rotor 3 and the sun gear 39 also rotates in unison with the turbine rotor 5 so that the rear planetary unit 39, 40. 4|, and 42 rotates as a unit. The power flow is still divided, one path being from the gear carrier 13 through the planet gears 80, ring gear 82-, pump rotor 4,- and stator 5 to the turbine rotor 6, and the other path being from the gear carrier 13 through the planet gears 80 and sun gear 3| to the turbine rotor 3. Under these conditions, a torque range of from 2.2:1 up to 1:1 may be obtained, 60 per cent of the power now being through the fluid torque converter. For high gear, both clutches 43 and 83 are connected. Under these conditions, there are I three power flow paths between the shafts I and the shaft 3, thesun gear 53 being held against rotation to effect overdrive of the ring gear 12 with respect to the gear carrier.

In the construction shown in Figs. 13, 14, 15, and 16, the parts I, 2,3, 4, 5, 8 ,39, 43, 40a, 41, 42, 45, 41, and 49 are similar in structure and function to the corresponding parts shown in Figs. 7, B, and 9. In Figs. 13-46, incL, however, means are provided for-dividing the power flow in two different places. In one place, power flow is divided so that one part flows to the p p rotor and another part to the turbine rotor. In another place, the power flow isdivided so that one branch of thepower flows to one of the gears of the rear planetary, by-passing the fluid torque converter, and the other part flows to the fluid torque converter.

For this purpose, in Figs. 13 and 14, a front planetary gear construction is provided comprising a gear carrier '13 connected to rotate with the 43 and are disconnected, providing two power flow paths. The fluid power flow path is from the gear carrier 13 through the planet gears Bil, ring gear 32, pump rotor 4, stator 5, turbine rotor 5, one-way clutch'l'l, shaft 3, sun gear 39, planet 1 gears 41, and cage 40 to thedriven shaft 3, the

ring gear 42 being held against rotation by the one-way anchorage 43. The nonfluid power flowpath is from the-gear carrier 13 through the planet gears ll, sun gear 8|, turbine hub, one- 2. One power flow path is from the shaft 1, through the clutch, shaft 3, sun gear 39, planet gears 41 and gear carrier to the shaft 2. An

other path is from the gearcarrier 19 through the planet gears 80, ring gear 82, pump rotor 4,

,efllciency of approximately 93 per cent, even if the fluid part of the transmission is only at per cent efliciency.

The construction of Fig. 14 is similar to that of Fig. 13 so far as the front clutch and front planetary construction are concerned. The rear planetary of Fig. 14 differs from the rear planetary of Fig. 13 in that the relations of the gears 39 and 42 are reversed. In Fig. 14, the sun gear 39, instead of being keyed to the shaft 3, is connectible and disconnectible with the turbine rotor 6 by means of the clutch 43. The ring gear 42, instead of being controlled by the clutch 43, as in Fig-13, is keyed to the shaft 3. The operation is similar to the operation described in connection with Fig. 13, though different torque and efficiency values are obtained. With the construction of Fig. 14, in low gear, the torque range will be from about 3.7:1 to about 1.6:1, .60 per cent of the power flow being through the hydraulic Part of the transmission. In the intermediate range, with the rear clutch 43 connected and the front clutch 33 disconnected, the torque rangewill be from approximately 2.2:1 to practically 1:1, 60 per cent of the power flow still being through the fluid part of the transmission. In the high range, with both clutches connected. the speed ratio range will be from about 1.3:1 to

operating practically direct, only 24 per cent of the power flow being through the fluid P rt Of the trans mission. Under these conditions, the overall emciency will be approximately 95 per cent, even if the efilciency of the fluid part of the transmission drops to 80 per cent.

The construction of Fig. 15 is similar to that of 13, except that the relations of the sun gear ill and ring gear 82 to the other parts of the transmission are reversed. In Fig. 15, the ring gear 82, instead of being connected tothe pump rotor 4, is connected to rotate with the turbine rotor and the sun gear Bl, instead of being connected to rotate with the turbine rotor B, is connected to rotate with the pump rotor l. The operation is in general the same as that described in connection with Fig. 13. In this form, in the low, speedrange, with both clutches l3 and 83 disconnected, the speed ratio range varies from 4.5:1 to 2.5: 1, in percent of the power flow being through the fluid torque converter. In the intermediate range, with the rear clutch 43 connected, the speed ratio range varies irom 1.8:1 to practically 1:1, 40 per cent of the power flow being through the fluid torque converter. In the high range, with both clutches l3 and 83 connected, the speed ratio range is from 1.35:1 to substantially 1:1, 24 per cent of the power flow being through the fluid torque converter. Under these conditions the overall emciency will approximate 95 per cent, even if the emciency of the fluid part of the transmission drops to 80 per cent.

The construction shown in Fig. 16 is similar to that shown in Fig. 15, except that the relations of the gears 39 and 12 are reversed. In Fig. 16, the sun gear 38, instead of being keyed to the shaft 3, is connectible and disconnectlble with respect to the turbinerotor t by means or the clutch 43, and the ring gear 42, instead of being controlled by the clutch 43, as in Fig. 15, is keyed disconnected, the speed ratio range varies from 3:1 to 1.66:1, 40 per cent of the power flow being throughthe fluid torque converter. In th intermediate stage. with the clutch" connected and the clutch I3 disconnected, the speed ratio range varies from 1.8:1 to substantially 1:1, 40

, Having thus describedmy invention, what I claim and desire to secure by Letters Patent is:

1. A turbo-planetary transmission comprising a drive shaft, a driven shaft, 2. pump rotor, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said gears and said turbine rotor being connected to rotate in unison with the driven shaft, clutch means for connecting and disconnecting said pump rotor with respect to the other of said gears, and clutch means for connecting and disconnecting said pump rotor with respect to said gear carrier.

2. A turbo-planetary transmission comprising a drive shaft, a driven'shaft, a pump rotor, 21 reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said gears and said turbine rotor bein connected to rotate in unison with the driven shaft, clutch means for connecting and disconnecting said pump rotor with respect to the other of said gears, clutch means for connecting and disconnecting said pump rotor with respect to said gear carrier, and anchorage means for holding said other of said gears against rotation in the direction of rotation of said gear carrier to effect overdrive of said one of said gears.

3. A. turbo-planetary transmission comprising a drive shaft, a driven shaft, a pump rotor, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, 9, sun gear per cent of the power flow being through the fluid torque converter. clutches l3 and 83 are connected, the speed ratio range will be from 1.2:1 to substantially direct drive, 16 per cent of the power flow being through the fluid torque converter. Under these conditions, the overall efliciency will be approximately 97 per cent even if the emcicncy or the fluid part of the transmission drops to 80 per cent.

In the construction of Figs. 1a and 16, a reverse may be obtained by means of a stationaryclutch ring 404 cooperating with the gear carrier ll in the manner described in connection with Fig. 8.

By proper choice of the relative diameters of ring gear and sun gear and a proper selection from thetypes of transmission shown in Figs.

In high gear, when bothv 13-16, incl, a wide variety or transmissions may beobtained, varying in torque. ratiofl, speed ranges, and overall efliciency. 7

Further modiflcationswill be apparent to those meshing with said planet gearing, a ring gear mounted with said planet gearing, said ring gear and said turbine rotor being connected to rotate in unison with the driven shaft, clutch means for connecting and disconnecting said pump rotor with respect to said sun gear, and clutch means for connecting and disconnecting said pump rotor with respect to said gear carrier.

4. A turbo-planetary transmission comprising a drive shaft, a driven shaft, a pump rotor, a reactance stator, a turbine rotor. a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, a sun gear meshing with said planet gearing, a ring gear meshing with said planet gearing, said ring gear and said turbine rotor being connected to rotate in unison with the driven shaft, clutch means for connecting and disconnecting said pump rotor with respect to said sun gear, clutch means for '5. A turbo-planetary transmission comprising a, drive shaft, a driven shaft, a pump rotor, a one-way rotatable reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said gears and said turbine rotor being connected to rotate in unison with .the driven shaft, clutch means for connecting skilled in the art and itis desired, therefore. that the inventionbe limited I respect to said gear carrier, a secondgear carrier rotatable with said driven shaft, planet gearing'mounted on said second gear carrier, two coaxial gears meshing with said planet gearing, one

a drive shaft, a driven shaft, a pump rotor; a one-way rotatable reactance stator, a turbine ro-'- tor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said of said last said coaxial gears being rotatable planet gearing, one of said gears and said turbine rotor being connected to rotate in unison with the driven shaft, clutch means for connecting and disconnecting said pump, rotor with respect to the other of said gears, clutch means for connecting and disconnecting said pump rotor with respect to said gear carrier, a second gear carrunning the intermediate shaft, and means for connecting and disconnecting the intermediate shaft with respect to the drive shaft.

10. A hydro planetary transmission comprising a drive shaft, a gear carrier connected to rotate in unison therewith, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, a, pump rotor connected to rotate in unison with one of said two gears, a turbine rotor rotatable in unison with the other of said gears, a reactance stator acting between said rotors, a driven shaft, 9, second gear carrier connected to rotate with said driven shaft, planet rier rotatable with said driven shaft, planet gearing mounted on said second gear carrier, two

coaxial gears meshing with said planet gearing, means for connecting and disconnecting one of said last said coaxial gears with respect to said with the other of said last said coaxial gears, and anchorage means for holding said oneof said last said gears against rotation in the direction of rotation of said gear carrier. w

'I. A turbo-planetary transmission comprising a drive shaft, a driven shaft, an intermediate shaft, a pump rotor driven from said drive shaft,

a reactance stator, a. turbine rotor, a gear carrierdisconnecting said drive shaft with respect to said intermediate shaft.

8. A turbo-planetary transmission comprising a drive shaft, a. driven shaft, an intermediate shaft, a pump rotor driven from said drive shaft, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the driven shaft, planet gearing mounted on asid gear carrier, two coaxial gears meshing with said planet gearing, one of said ears being connected to rotate with said intermediate shaft, means for connecting and disconnecting said turbine rotor'with respect to the other of said gears, one-way anchorage means for preventing reverse rotation of said other of said gears as said one of said gears rotates, clutch means for connecting and disconnecting said turbine rotor withrespect to said intermediate shaft, and clutch means for connecting and disconnecting said drive shaft with respect to said intermediate shaft. I

9. A hydro planetary transmission comprising a drive shaft, a driven shaft, and an intermediate shaft, said shafts being coaxial, a. pump rotor .driven from said drive shaft, a turbine rotor, a reactance stator acting between said pump rotor and turbine'rotor, a gear carrier connected to rotate in unison with said driven shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said coaxial gears being connected to rotate in unison with said' intermediate shaft, the other of said gears being connected to rotate in unison with the turbine rotor, one-way coupling means for preventing the turbine rotor from overone-way rotatable stator, a. third shaft rotatable gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one-waycoupling means for preventing reverse rotation of one of said last two gears as the other of said last two gears rotates, coupling means for connecting and disconnecting said one oi-said last two gears with respect to the turbine rotor and its associated gear, clutch means for connectin and disconnecting the other of the last said two gears with respect to the drive shaft, and oneway coupling means for. preventing the turbine rotor from overrunning said other of the last said two gears. s

' 11. A turbo-planetary transmission comprisinga drive shaft, a driven shaft, a pump rotor, a reactance stator, a turbine rotor, a gear carrier'connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said gears and said turbine rotor being. connected to rotate with the driven shaft, clutch means for connecting and disconnecting said ipump rotor with respect to the other of said gears, and clutch means for connecting and disconnecting said pump rotor with respect to said drive shaft.

12; A turbo-planetary transmission comprising a, drive shaft, a driven shaft, a pump rotor, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft,

planet gearing mounted on said gear carrier,

and driven shaft comprising means by which in one condition the pump rotor is connected to rotate in unison with the drive shaft and is supplied with power therefrom and the two gears are disconnected from driving relation with respect to the driven shaft and by which in another condition the pump rotor is not connected to rotate in unison with the drive shaft and is rotatable in unison with and supplied with power from one of said gears and the driven shaft is rotatable in unison with and supplied with power from the other of said gears as well as from said turbine rotor. V

13. A turbo-planetary transmission comprising a drive shaft, a driven shaft, 9. pump rotor,

a reactancestator, aturbine rotor, a gear carrier connected to rotate with the drive shaft,

planet gearing mounted on said gear carrier, a sun gear and a ring gear meshing with said planet gearing, said turbine rotor being connected to rotate with the drivenshaft, and means including rotation-controlling instrumentalities for changing the speed ratio condition between the drive shaft and driven shaft comprising means by which in one condition the pump rotor is connected to rotate in unison with the drive shaft and is supplied with power therefrom and the two gears are disconnected from driving relation with respect to the driven shaft and by which in another condition the pump rotor is not connected to rotate in unisonwith the drive shaft and is.

rotatable in unison with and supplied with power from said ring gear and the driven shaft is rotatable in unison with, and supplied 'withpower from saidsun gear as well as from said turbine rotor.

14. A turbo-planetary transmission comprising a drive shaft, adriven shaft, a pump rotor, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, said turbine rotor being connected to rotate with the driven shaft, and means including rotation-controlling instrumentalities for changing the speed ratio condition between the drive shaft and driven shaft comprising means by which in one condition all the power from the drive shaft to the driven shaft is through the pump rotor, reactance stator and turbine rotor, and by which in another condition one of the gears is connected to rotate in unison with the pump rotor and supplies power thereto and the other gear is connected to rotate in unison with the driven shaft and supplies power thereto in addition to power supplied thereto by said turbine rotor.

15. A turbo-planetary transmission comprising a drive shaft, a driven shaft, a pump rotor, a reactance stator, a turbine rotor, a gear carrier connected to rotate with the drive shaft. planet gearing mounted on said gear carrier, a sun gear and a ring gear meshin with said planet gearing, said turbine rotor being connected to rotate with the driven shaft, and means including rotationcontrolling instrumentalities for changing the 6 speed ratio condition between'the drive shaft and driven shaft comprising means by which in one condition all the power from the drive shaft to the driven shaft is through the pumprotor, reactance stator and turbine rotor and by which in another 1 condition the ring g ar is connected to rotate in 15 said turbine rotor. 16. A turbo-planetary transmission comprising a drive shaft, a driven shaft, an intermediate shaft, 8. pump rotor, driven from said drive shaft, a reactance stator, a. turbine rotor, a gear carrier 20 connected to rotate with the driven shaft, planet gearing mounted on said gear carrier, two coaxial gears meshing with said planet gearing, one of said gears being connected to rotate with said intermediate shaft, means for connecting anddis- 25 connecting said turbine rotor with respect to the other of said gears, means for preventing reverse rotation of said other of said gears as said one of said gearsrotates, means connecting said turbine rotor in driving relation with respect to said intermediate shaft, and clutch means for connecting and disconnecting said drive shaft with respect to said intermediate shaft.

5 WILLARD n- POLLARD. 

